Duplex variable plunger pump

Abstract

The utility model belongs to the technical field of variable displacement piston pumps, and particularly relates to a duplex variable displacement piston pump. The double-pump variable displacement mechanism comprises a double pump and a variable displacement mechanism assembly, the variable displacement mechanism assembly and the double pump are designed to be of a split type structure, and the variable displacement mechanism assembly is used for conducting variable adjustment on the oil suction amount of the double pump. The duplex pump comprises a cylinder body, a transmission shaft, a front swash plate and a rear swash plate; a central through hole is formed in the cylinder body, and the transmission shaft is arranged in the central through hole; the front end and the rear end of the cylinder body are each provided with a plunger cavity, and a plunger assembly is installed in each plunger cavity. The plunger assembly at the front end of the cylinder body is connected with the transmission shaft through a front swash plate, and the plunger assembly at the rear end of the cylinder body is connected with the transmission shaft through a rear swash plate. The plate surface of the front swash plate and the plate surface of the rear swash plate are arranged in the same vertical plane at an included angle; in the working process, the transmission shaft rotates to drive the plunger assembly to do linear reciprocating motion in the plunger cavity of the cylinder body, and then hydraulic energy is conveniently provided for the servo mechanism.

Description

Technical Field

[0001] This utility model belongs to the field of variable displacement piston pump technology, specifically relating to a dual variable displacement piston pump. Background Technology

[0002] Variable displacement piston pumps are the power components of hydraulic servo mechanisms. Existing external variable displacement piston pumps are generally mounted externally to the hydraulic servo mechanism via flanges. These not only occupy a large space and have a complex structure, but also have numerous sealing components and poor sealing reliability, making it difficult to meet the development requirements of miniaturization, lightweighting, integration, long-term operation, and long-term storage of hydraulic servo mechanisms. Existing embedded variable displacement piston pumps are single-unit, half-shaft variable displacement pumps, which are not only difficult to manufacture and have low operational reliability, but also have low overall pump technology maturity and have not yet achieved mass production.

[0003] With the rapid development of missiles with high requirements for weight and size, the integrated electro-hydraulic servo mechanisms equipped with them have increasingly higher requirements in terms of lightweight, miniaturization, high specific power, technological maturity, manufacturing process and reliability. Existing external and embedded variable displacement piston pumps can no longer meet the development needs of integrated electro-hydraulic servo mechanisms. Utility Model Content

[0004] The purpose of this invention is to address the problem that existing external and embedded variable displacement piston pumps can no longer meet the development needs of integrated electro-hydraulic servo mechanisms due to the rapid development of missiles with high requirements for weight and size. This invention provides a dual variable displacement piston pump that simplifies the overall layout of the variable displacement pump and realizes the design concept of lightweight and miniaturization.

[0005] A dual variable displacement piston pump includes a dual pump and a variable displacement mechanism assembly;

[0006] The variable mechanism assembly and the dual pump adopt a separate structure design, and the variable mechanism assembly is used to adjust the oil suction volume of the dual pump.

[0007] The dual pump includes a cylinder block, a drive shaft, a front swashplate, a rear swashplate, a front cover, and a rear cover. The cylinder block has a central through-hole, and the drive shaft is disposed within this central through-hole. The sidewalls of the cylinder block have an oil outlet and an oil suction hole. The front and rear ends of the cylinder block each have plunger chambers, and each plunger chamber contains a plunger assembly. The plunger assembly at the front end of the cylinder block is connected to the drive shaft via the front swashplate, and the plunger assembly at the rear end of the cylinder block is connected to the drive shaft via the rear swashplate. The surfaces of the front and rear swashplates are angled together in the same vertical plane. The rear cover seals the rear end of the cylinder block. The front cover has a through-hole for the drive shaft to pass through, and the front cover is disposed at the front end of the cylinder block, with a bearing between the front cover and the drive shaft. The front cover and the drive shaft are sealed together by a sealing assembly.

[0008] During operation, the rotation of the drive shaft drives the front and rear swashplates to rotate, thereby driving the piston assembly to perform linear reciprocating motion within the piston chamber of the cylinder. When the piston assembly performs linear reciprocating motion within the piston chamber of the cylinder, the piston assembly can discharge pressurized oil from the piston chamber through the oil outlet and draw in pressurized oil through the oil suction port, thereby providing hydraulic energy to the servo mechanism.

[0009] Furthermore, the dual pump also includes a return plate, the piston assembly is connected to the front swashplate via the return plate, and the piston assembly is connected to the rear swashplate via the return plate; a ball joint sleeve is provided between the drive shaft and the central through hole of the cylinder block, the ball joint sleeve is sleeved on the drive shaft, the return plate has a ball joint through hole, and the ball joint sleeve and the ball joint through hole form a ball joint fit.

[0010] Furthermore, the dual pump also includes an adjusting shim set, which comprises multiple adjusting shims of varying thicknesses, each of which is used to adjust the position of the ball head sleeve relative to the cylinder body.

[0011] Furthermore, a one-way valve is provided in the oil outlet hole on the side wall of the cylinder.

[0012] Furthermore, the dual pump has five plunger assemblies installed at the front and rear ends of the cylinder block, respectively.

[0013] Furthermore, the front swashplate is connected to the drive shaft by a pin, and the rear swashplate is also connected to the drive shaft by a pin.

[0014] Furthermore, the variable mechanism assembly includes a housing with an internal cavity, one end of which is connected to the oil outlet of the dual pump and the other end of which is connected to the oil suction port of the dual pump.

[0015] The cavity of the housing is provided with a first valve core, and a force balancing component is provided between the first valve core and the cavity wall of the housing; a first valve sleeve is sleeved on one end of the first valve core, and a second valve core is connected to the other end of the first valve core; the second valve core is connected to the cavity wall of the housing through a second valve sleeve sleeved on the second valve core; an oil suction port is provided on the housing, and the oil suction port is connected to the oil suction hole of the dual pump through the oil suction window of the first valve sleeve;

[0016] In use, the force balancing component automatically adjusts the position of the first valve core in the first valve sleeve by the magnitude of the force at the oil outlet of the dual pump, thereby changing the oil suction window area of ​​the first valve sleeve.

[0017] Furthermore, the first valve sleeve is disposed at one end for connecting to the oil suction port of the dual pump, and the oil suction window area of ​​the first valve sleeve decreases when the first valve core moves toward the first valve sleeve.

[0018] Furthermore, by moving the position of the first valve core within the first valve sleeve, the cross-sectional area of ​​the flow channel between the oil inlet and the first valve sleeve is changed.

[0019] Furthermore, the force balancing component is a spring.

[0020] The beneficial effects of this utility model are as follows:

[0021] This invention provides a dual variable displacement piston pump. The variable displacement mechanism assembly and the dual pump are designed as separate units, which facilitates structural layout and functional expansion. This allows the dual pump to achieve constant pressure operation when the variable displacement mechanism assembly is engaged, and to function as a fixed displacement pump when the variable displacement mechanism assembly is not engaged. Furthermore, the dual variable displacement piston pump provided by this invention is an embedded, dual, through-shaft variable displacement piston pump, which is not only small in size and light in weight, but also has high power output, high sealing reliability, low processing difficulty, good manufacturability, and low production cost. The dual variable displacement piston pump provided by this invention has high operational reliability, high overall pump technology maturity, has achieved mass production, and has generated and will continue to generate significant economic benefits. Attached Figure Description

[0022] Figure 1 This is a schematic cross-sectional view of a dual pump.

[0023] Figure 2 This is a cross-sectional structural diagram of the variable mechanism component.

[0024] Figure 3 This is a schematic diagram of the front swashplate.

[0025] Figure label:

[0026] 1-First valve sleeve, 2-First valve core, 3-Force balancing component, 4-Housing, 5-Second valve core, 6-Second valve sleeve, 7-Rear cover, 8-Rear swash plate, 9-Return plate, 10-Cylinder block, 11-Plunger assembly, 12-Front swash plate, 13-Bearing, 14-Front cover, 15-Sealing assembly, 16-Pin, 17-Drive shaft, 18-Adjusting shim assembly, 19-Ball head sleeve, 20-Oil suction area, 21-Distribution groove, 22-Oil discharge area. Detailed Implementation

[0027] Exemplary embodiments will be described more fully below with reference to the accompanying drawings; however, these exemplary embodiments may be embodied in different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this invention will be thorough and complete, and will enable those skilled in the art to fully understand the scope of this invention.

[0028] Where there is no conflict, the embodiments of this utility model and the features thereof can be combined with each other.

[0029] As used herein, the term “and / or” includes any and all combinations of one or more related enumerated entries.

[0030] The terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the scope of the invention. The singular forms “a” and “the” used herein are also intended to include the plural forms unless the context clearly indicates otherwise.

[0031] When the terms “comprising” and / or “made of” are used in this specification, the presence of the stated feature, integral, step, operation, element and / or component is specified, but the presence or addition of one or more other features, integrals, steps, operations, elements, components and / or groups thereof is not excluded.

[0032] Unless otherwise specified, all terms used herein (including technical and scientific terms) have the same meaning as commonly understood by one of ordinary skill in the art. It will also be understood that terms such as those defined in commonly used dictionaries should be understood to have the meaning consistent with their meaning in the context of the relevant art and the present invention, and will not be understood to have an idealized or overly formal meaning unless expressly so defined herein.

[0033] In response to the rapid development of missiles with high requirements for weight and size, existing external and embedded variable displacement piston pumps can no longer meet the development needs of integrated electro-hydraulic servo mechanisms. This embodiment provides a dual variable displacement piston pump, which can simplify the overall layout of the variable displacement pump and realize the design concept of lightweight and miniaturization.

[0034] like Figures 1 to 3 As shown, this embodiment provides a dual variable displacement piston pump with an embedded mounting structure, including a dual pump and a variable displacement mechanism assembly; wherein, the dual pump includes a cylinder block 10, a drive shaft 17, a piston assembly 11, a front swashplate 12, a rear swashplate 8, a return plate 9, a front cover 14, a rear cover 7, and a sealing assembly 15.

[0035] In the tandem pump, the cylinder body 10 has a central through hole, and the drive shaft 17 of the tandem pump is disposed within this central through hole. Piston chambers are respectively provided at the front and rear ends of the cylinder body 10, and the plunger assembly 11 of the tandem pump is installed within these plunger chambers. It should be understood that the number of plunger assemblies 11 in the tandem pump can be selected appropriately according to actual conditions. For example, the tandem pump can have five plunger chambers at the front and rear ends of the cylinder body 10, so that five plunger assemblies 11 can be installed at the front and rear ends of the cylinder body 10. In the tandem pump of this embodiment, the side wall of the cylinder body 10 is provided with an oil outlet and an oil suction port. During operation, the plunger assembly 11 is used to discharge high-pressure oil from the plunger chamber through the oil outlet, and the plunger assembly 11 is used to draw in low-pressure oil through the oil suction port. It should be understood that, in this embodiment, high-pressure oil and low-pressure oil refer to two types of oil with relatively high and low pressure states in the plunger cavity when the plunger assembly 11 makes linear reciprocating motion in the plunger cavity during operation.

[0036] In the tandem pump of this embodiment, the plunger assembly 11 is connected to the drive shaft 17 via the front swashplate 12 and the return plate 9, or the plunger assembly 11 is connected to the drive shaft 17 via the rear swashplate 8. Specifically, in Figure 1 In the view shown, the right side of the cylinder body 10 is the front end of the cylinder body 10. The plunger assembly 11 at the front end of the cylinder body 10 is connected to the drive shaft 17 via a return plate 9 and a front swashplate 12, and the front swashplate 12 is connected to the drive shaft 17 via a pin 16. Correspondingly, the left side of the cylinder body 10 is the rear end of the cylinder body 10. The plunger assembly 11 at the rear end of the cylinder body 10 is connected to the drive shaft 17 via a return plate 9 and a rear swashplate 8, and the rear swashplate 8 is connected to the drive shaft 17 via a pin 16. In the tandem pump of this embodiment, the plate surface of the front swashplate 12 and the plate surface of the rear swashplate 8 are arranged at an angle in the same vertical plane, so that when the tandem pump of this embodiment is working, the plunger assemblies 11 on the same side of the drive shaft 17 can move in the same way.

[0037] Furthermore, during operation, the return plate 9 can be rotated by rotating the drive shaft 17 via the front swashplate 12 or the rear swashplate 8. When the drive shaft 17 rotates at high speed, it drives the front swashplate 12 and the rear swashplate 8 to rotate. Because the working surfaces of the front swashplate 12 and the rear swashplate 8 have a fixed angle, the plunger assembly 11 can perform linear reciprocating motion within the plunger cavity of the cylinder block 10 under the action of the front swashplate 12, the rear swashplate 8, and the return plate 9.

[0038] In this embodiment, the rear cover 7 is installed at the rear end of the cylinder body 10, and a bearing 13 is provided between the rear cover 7 and the drive shaft 17. The front cover 14 in this embodiment has a through hole to allow the drive shaft 17 to pass through it. The front cover 14 in this embodiment is installed at the front end of the cylinder body 10, and a bearing 13 is provided between the front cover 14 and the drive shaft 17; simultaneously, the front cover 14 and the drive shaft 17 are sealed together by a sealing assembly 15.

[0039] In this embodiment, the front swashplate 12 and the rear swashplate 8 can adopt the same structure. Preferably, the structure of the front swashplate 12 and the rear swashplate 8 can adopt the swashplate structure disclosed in patent number CN20847054U, entitled "An Embedded Miniature Variable Pump for an Electro-hydraulic Servo Mechanism". Specifically, as... Figure 3 As shown, the front swashplate 12 or the rear swashplate 8 may be provided with an oil suction area 20, an oil discharge area 22 and a distribution groove 21.

[0040] Further, such as Figure 1 As shown, in this embodiment, a ball joint sleeve 19 is provided between the drive shaft 17 and the central through hole of the cylinder 10, and a ball joint through hole is provided on the return plate 9; the ball joint sleeve 19 is sleeved on the drive shaft 17, and the ball joint sleeve 19 and the ball joint through hole form a ball joint fit. During operation, as the drive shaft 17 rotates continuously, the plunger assembly 11 can perform linear reciprocating motion in the plunger cavity within the cylinder 10, so that the dual pump can continuously draw in low-pressure oil and discharge high-pressure oil, thereby providing hydraulic energy to the servo mechanism.

[0041] Furthermore, the tandem pump in this embodiment also includes an adjusting shim group 18, which comprises multiple adjusting shims of varying thicknesses. Each adjusting shim is used to adjust the position of the ball head sleeve 19 relative to the cylinder block 10, thereby achieving the adjustment and maintenance of the clearance between the plunger assembly 11 and the front swashplate 12, and facilitating the adjustment and maintenance of the clearance between the plunger assembly 11 and the rear swashplate 8. This allows the tandem pump structure in this embodiment to not only save radial installation space but also achieve a constant clearance return stroke. Moreover, the constant clearance return stroke structure can also meet the high-speed, high-pressure operating requirements of a variable pump.

[0042] Furthermore, in this embodiment, a one-way valve is provided in the oil outlet hole on the side wall of the cylinder 10.

[0043] In this embodiment, the variable displacement mechanism is used to adjust the oil intake of the tandem pump. In this embodiment, the variable displacement mechanism and the tandem pump are designed as separate units to facilitate better structural layout and functional expansion. This allows the tandem pump in this embodiment to achieve constant pressure operation when the variable displacement mechanism is involved, and to function as a fixed displacement pump when the variable displacement mechanism is not used.

[0044] Specifically, such as Figure 2 As shown, the variable mechanism component in this embodiment includes a housing 4 with an internal cavity. One end of the cavity is connected to the oil outlet in the dual pump, and the other end is connected to the oil suction port in the dual pump. The housing 4 is also provided with an oil suction port, which is connected to the cavity inside the housing 4.

[0045] exist Figure 2 In the view shown, in the variable displacement mechanism assembly, a first valve core 2 is provided within the cavity of the housing 4, and a force balancing member 3 is provided between the first valve core 2 and the cavity wall of the housing 4. In the variable displacement mechanism assembly, a first valve sleeve 1 is fitted over one end of the first valve core 2, and a second valve core 5 is connected to the other end. The second valve core 5 is connected to the cavity wall of the housing 4 via a second valve sleeve 6 fitted over it. Furthermore, in use, the oil suction window area of ​​the first valve sleeve 1 can be changed by adjusting the position of the first valve core 2 within the first valve sleeve 1.

[0046] Specifically, the first valve sleeve 1 is disposed at the end for connection with the oil outlet of the dual pump, and when the first valve core 2 moves toward the first valve sleeve 1, the oil suction window area of ​​the first valve sleeve 1 is reduced. In this embodiment, the force balancing member 3 can be a spring.

[0047] Preferably, if Figure 2 As shown, in the variable mechanism assembly, the oil inlet is connected to the oil suction port of the dual pump through the oil suction window of the first valve sleeve 1, and the cross-sectional area of ​​the flow channel between the oil inlet and the first valve sleeve 1 can be changed by moving the position of the first valve core 2 inside the first valve sleeve 1.

[0048] In operation, when the force exerted by the feedback high-pressure oil on the second valve core 5 is greater than the force exerted by the force balancing member 3 on the first valve core 2, the second valve core 5 pushes the first valve core 2 to move within the first valve sleeve 1 until the forces on the first valve core 2 are balanced. At this time, the area of ​​the oil suction window in the first valve sleeve 1 decreases due to the movement of the first valve core 2 within the first valve sleeve 1, thus reducing the oil suction volume of the tandem pump. When the force exerted by the feedback high-pressure oil on the second valve core 5 is less than the force exerted by the force balancing member 3 on the first valve core 2, the first valve core 2 pushes the second valve core 5 to move within the second valve sleeve 6 until the forces on the first valve core 2 are balanced. At this time, the area of ​​the oil suction window in the first valve sleeve 1 increases due to the movement of the first valve core 2 within the first valve sleeve 1, increasing the oil suction volume of the tandem pump, thereby fulfilling the variable requirements of the servo mechanism for the tandem pump.

[0049] Example embodiments have been disclosed herein, and while specific terminology has been used, it is for general illustrative purposes only and should not be construed as limiting. In some embodiments, it will be apparent to those skilled in the art that features, characteristics, and / or elements described in connection with particular embodiments may be used alone, or in combination with features, characteristics, and / or elements described in connection with other embodiments, unless otherwise expressly indicated. Therefore, those skilled in the art will understand that various changes in form and detail may be made without departing from the scope of the invention as set forth in the appended claims.

Claims

1. A dual variable displacement piston pump, characterized in that: Includes a tandem pump and variable displacement mechanism assembly; The variable mechanism assembly and the dual pump adopt a separate structure design, and the variable mechanism assembly is used to adjust the oil suction volume of the dual pump. The dual pump includes a cylinder block, a drive shaft, a front swashplate, a rear swashplate, a front cover, and a rear cover. The cylinder block has a central through-hole, and the drive shaft is disposed within this central through-hole. The sidewalls of the cylinder block have an oil outlet and an oil suction hole. The front and rear ends of the cylinder block each have plunger chambers, and each plunger chamber contains a plunger assembly. The plunger assembly at the front end of the cylinder block is connected to the drive shaft via the front swashplate, and the plunger assembly at the rear end of the cylinder block is connected to the drive shaft via the rear swashplate. The surfaces of the front and rear swashplates are angled together in the same vertical plane. The rear cover seals the rear end of the cylinder block. The front cover has a through-hole for the drive shaft to pass through, and the front cover is disposed at the front end of the cylinder block, with a bearing between the front cover and the drive shaft. The front cover and the drive shaft are sealed together by a sealing assembly. During operation, the rotation of the drive shaft can drive the front and rear swashplates to rotate, thereby driving the piston assembly to perform linear reciprocating motion within the piston chamber of the cylinder block. Furthermore, when the plunger assembly reciprocates linearly in the plunger chamber within the cylinder, the plunger assembly can discharge pressurized oil from the plunger chamber through the oil outlet and draw in pressurized oil through the oil suction port, thereby providing hydraulic energy to the servo mechanism.

2. The dual variable displacement piston pump according to claim 1, characterized in that: The dual pump also includes a return plate, the piston assembly is connected to the front swashplate via the return plate, and the piston assembly is connected to the rear swashplate via the return plate; a ball joint sleeve is provided between the drive shaft and the central through hole of the cylinder block, the ball joint sleeve is sleeved on the drive shaft, the return plate has a ball joint through hole, and the ball joint sleeve and the ball joint through hole form a ball joint fit.

3. The dual variable displacement piston pump according to claim 2, characterized in that: The dual pump also includes an adjusting shim set, which comprises multiple adjusting shims of varying thicknesses, each used to adjust the position of the ball head sleeve relative to the cylinder body.

4. The dual variable displacement piston pump according to claim 1, characterized in that: A one-way valve is provided in the oil outlet hole on the side wall of the cylinder.

5. The dual variable displacement piston pump according to claim 1, characterized in that: The dual pump has five plunger assemblies installed at the front and rear ends of the cylinder block, respectively.

6. The dual variable displacement piston pump according to claim 1, characterized in that: The front swashplate is connected to the drive shaft by a pin, and the rear swashplate is also connected to the drive shaft by a pin.

7. The dual variable displacement piston pump according to any one of claims 1-6, characterized in that: The variable mechanism assembly includes a housing with an internal cavity, one end of which is connected to the oil outlet of the dual pump and the other end of which is connected to the oil suction port of the dual pump. The cavity of the housing is provided with a first valve core, and a force balancing component is provided between the first valve core and the cavity wall of the housing; a first valve sleeve is sleeved on one end of the first valve core, and a second valve core is connected to the other end of the first valve core; the second valve core is connected to the cavity wall of the housing through a second valve sleeve sleeved on the second valve core; an oil suction port is provided on the housing, and the oil suction port is connected to the oil suction hole of the dual pump through the oil suction window of the first valve sleeve; In use, the force balancing component automatically adjusts the position of the first valve core in the first valve sleeve by the magnitude of the force at the oil outlet of the dual pump, thereby changing the oil suction window area of ​​the first valve sleeve.

8. The dual variable displacement piston pump according to claim 7, characterized in that: The first valve sleeve is disposed at one end for connecting to the oil suction port of the dual pump, and the oil suction window area of ​​the first valve sleeve decreases when the first valve core moves toward the first valve sleeve.

9. The dual variable displacement piston pump according to claim 7, characterized in that: The cross-sectional area of ​​the flow channel between the oil inlet and the first valve sleeve is changed by moving the position of the first valve core within the first valve sleeve.

10. The dual variable displacement piston pump according to claim 7, characterized in that: The force balancing component is a spring.

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